EP1722176A2 - Differential pressure valve - Google Patents

Differential pressure valve Download PDF

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Publication number
EP1722176A2
EP1722176A2 EP06009027A EP06009027A EP1722176A2 EP 1722176 A2 EP1722176 A2 EP 1722176A2 EP 06009027 A EP06009027 A EP 06009027A EP 06009027 A EP06009027 A EP 06009027A EP 1722176 A2 EP1722176 A2 EP 1722176A2
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EP
European Patent Office
Prior art keywords
differential pressure
pressure valve
throttle
valve according
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP06009027A
Other languages
German (de)
French (fr)
Other versions
EP1722176A3 (en
Inventor
Achim Dr.-Ing. Wiebelt
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Mahle Behr GmbH and Co KG
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Behr GmbH and Co KG
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Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1722176A2 publication Critical patent/EP1722176A2/en
Publication of EP1722176A3 publication Critical patent/EP1722176A3/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F25B41/33—Expansion valves with the valve member being actuated by the fluid pressure, e.g. by the pressure of the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/06—Details of flow restrictors or expansion valves
    • F25B2341/063—Feed forward expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2505—Fixed-differential control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Definitions

  • the invention relates to a differential pressure valve (delta-P valve), in particular for an expansion element of a Kraftmiliaaniage, according to the preamble of claim 1.
  • delta-P valve differential pressure valve
  • a known differential pressure valve 101 is shown as a schematic diagram.
  • the flow of refrigerant through a throttle point 102 by means of a valve pin 103 is controlled with a conical head 104 in conjunction with a spring 105 schematically indicated in the drawing.
  • the pressures in the spaces or flow channels separated by the restriction 102 are indicated by HD (high pressure side) and SD (suction pressure side), with the normal flow direction from the high pressure side HD to the suction pressure side SD.
  • the head 104 is in this case arranged suction pressure side and the shaft of the valve pin 103 penetrates the throttle opening.
  • the spring 105 is arranged on the high pressure side.
  • a disadvantage of this known differential pressure valve is that there is a nearly linear relationship between the free flow cross-section and the applied pressure difference, which is not desirable in all applications.
  • check valves are known in which a valve ball biased by a spring in the closed state abuts a valve seat which is formed by a conical or cylindrical throttle opening, and in the open state under compression of the spring releases a flow opening.
  • check valves usually show a very different from the requirements for refrigerant circuits opening behavior.
  • differential pressure valve in particular for an expansion device of an automotive air conditioning system for controlling a flow of a fluid in response to a pressure difference, which is applied between the high pressure side and the suction pressure side of the differential pressure valve, proposed, wherein the differential pressure valve, a throttle element which regulates the flow through a throttle point, and a spring which biases the throttle element in the closing direction, and in which the throttle element and spring are designed and arranged such that a disproportionate dependence of the passage cross section on the applied pressure difference results.
  • This differential pressure valve allows for high pressure differences due to the disproportionately large flow cross section and a larger Cooling capacity. It is relatively inexpensive to produce. In addition, the valve can work self-regulating. It can therefore be dispensed with electronic controls, sensors, electrically adjustable valves, etc.
  • a differential pressure valve in particular for an expansion element of an automotive air conditioning, for controlling a flow of a fluid in response to a pressure difference, which is applied between the high pressure side and the suction pressure side of the differential pressure valve, proposed wherein the differential pressure valve, a throttle element that regulates the flow through a throttle point, and a biasing the throttle element in the closing direction spring, and wherein the throttle element has a spherical head.
  • This training can be advantageous either alone or in combination with the above-mentioned dependence on the passage cross-section and pressure difference.
  • this differential pressure valve allows for high pressure differences due to the disproportionately large flow cross section and a larger cooling capacity. It is relatively inexpensive to produce. This valve can also be self-regulating in the above sense.
  • the throttle element of the differential pressure valve may have a shaft.
  • the shaft of the throttle element is preferably cylindrical.
  • the head of the throttle element is preferably mounted centered on the shaft by means of an adhesive connection. However, it may also prove advantageous to design the head and shaft of the throttle element in one piece.
  • the shaft preferably has a diameter of less than 2 mm.
  • the ball diameter of the throttle elements are preferably between 1.5 and 2.0 mm, the shaft is dimensioned correspondingly smaller. Since a high manufacturing accuracy for the head is required in particular balls from the ball bearing manufacturing, which are relatively inexpensive to obtain at high accuracies, suitable.
  • the difference in diameter of the spherical head and the throttle opening to be closed by the latter is preferably not more than 0.01 mm, in particular in the case of the aforementioned ball diameters. Also 0.005 mm, 0.0075 mm, 0.015 mm or 0.02 mm are conceivable.
  • the ratio of ball diameter to throttle opening diameter is less than 1.02. If the ratio is less than 1, then the head of the throttle element penetrates into the throttle opening, which is why an axial stop is provided, for example on the shaft. However, due to possible jamming and jamming, a ratio of ball diameter to throttle opening diameter of 1.0 is unlikely without other measures. Incidentally, ratios of 1.01, 1.03, 1.04, 1.05 or 1.1 are also conceivable.
  • the head of the throttle element is preferably arranged on the suction pressure side, wherein the shaft of the throttle element extends away from the throttle opening, so that the shaft does not protrude through the throttle opening.
  • the throttle cross-section is preferably disproportionately greater for large pressure differences than for small pressure differences, so that at maximum power requirement and sufficient fluid can flow through the differential pressure valve.
  • a serving as an expansion element in a motor vehicle air conditioning differential pressure valve 1 has to control the refrigerant flow (refrigerant present R744) a throttle point 2, the throttle point 2 by a spherical shaped end of a valve pin 3, which rests tightly against the presently cylindrical throttle opening in the closed state , is formed.
  • the diameter difference between the throttle opening and the ball is 0.005 mm with a ball diameter of 2 mm.
  • the valve pin 3 has said spherical end, hereinafter referred to as head 4, in the area of the dripping point 2 and a cylindrical shaft connected therewith by adhesive, which extends away from the throttle point 2, ie does not protrude into the throttle opening.
  • the shaft has in this case a diameter of 1.5 mm.
  • a spring 5 is attached with its one end, which has a closing force the valve pin 3 exerts, so that in the absence or low pressure difference, the throttle opening is closed by the head 4 of the valve pin 3 as a result of an at least substantially fluid-tight contact of the corresponding conical portion of the valve pin 3 on the valve seats (see highly schematic representation of FIG. 1).
  • the spring 5 is loaded on pressure.
  • COP coefficient of performance
  • the characteristic curve of a differential pressure valve 1 according to the invention with spherical end in conjunction with a spring with the spring constant of 23 N / mm in the range of low differential pressures near the upper range limit, imd in the course of the curve is approximately centered.
  • the characteristics of conventional differential pressure valves 101 with a conical head 104 run in the form of a straight line, so that, depending on the spring constant, a region always runs outside the optimum range. This characteristic not only makes it possible to achieve a significantly improved cooling capacity, but also in the case of a high demand for refrigerant throughput, ie in high-load operation.
  • valve pin 3 shifts against the spring force in the direction of the suction pressure side SD and the throttle point 2 opens gradually.
  • the throttle opening is released much faster due to the geometry of the head 4, so that a non-linear relationship between the pressure difference and the released flow cross-section, which is related to the flow rate results (see Fig. 2).
  • the diameter of the head is smaller than the diameter of the throttle opening, so that the head can completely penetrate into the throttle opening.
  • a flange-like stop is provided, which limits the movement and closes the throttle opening in the end position.
  • an always existing residual opening can be realized, for example, to avoid an excessive local pressure increase when switching off the air conditioning, as they can be a problem especially in CO 2 refrigerant circuits.

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  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Temperature-Responsive Valves (AREA)

Abstract

The differential pressure valve regulates a flow of a fluid in dependence of a difference of pressure. A differential pressure valve has a flow control element, which regulates the flow through a throttle point (2), and a spring (5) which links the flow control element up (3) in a closing direction. The flow control element and spring are arranged in such a way that a super proportional dependence of the passage cross section results on a close pressure difference.

Description

Die Erfindung betrifft ein Differenzdruckventil (Delta-P-Ventil), insbesondere für ein Expansionsorgan einer Kraftfahrzeugklimaaniage, gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a differential pressure valve (delta-P valve), in particular for an expansion element of a Kraftfahrzeugklimaaniage, according to the preamble of claim 1.

In Fig. 3 ist ein bekanntes Differenzdruckventil 101 als Prinzipskizze dargestellt. Hierbei wird der Durchfluss von Kältemittel durch eine Drosselstelle 102 mit Hilfe eines Ventilstifts 103 mit einem konischen Kopf 104 in Verbindung mit einer in der Zeichnung schematisch angedeuteten Feder 105 geregelt. Die Drücke in den durch die Drosselstelle 102 getrennten Räumen oder Strömungskanälen sind durch HD (Hochdruckseite) und SD (Saugdruckseite) bezeichnet, wobei die normale Strömungsrichtung von der Hochdruckseite HD zur Saugdruckseite SD verläuft. Der Kopf 104 ist hierbei saugdruckseitig angeordnet und der Schaft des Ventilstifts 103 durchdringt die Drosselöffnung. Die Feder 105 ist hochdruckseitig angeordnet.In Fig. 3, a known differential pressure valve 101 is shown as a schematic diagram. Here, the flow of refrigerant through a throttle point 102 by means of a valve pin 103 is controlled with a conical head 104 in conjunction with a spring 105 schematically indicated in the drawing. The pressures in the spaces or flow channels separated by the restriction 102 are indicated by HD (high pressure side) and SD (suction pressure side), with the normal flow direction from the high pressure side HD to the suction pressure side SD. The head 104 is in this case arranged suction pressure side and the shaft of the valve pin 103 penetrates the throttle opening. The spring 105 is arranged on the high pressure side.

Nachteilig bei diesem bekannten Differenzdruckventil ist, dass ein nahezu linearer Zusammenhang zwischen dem freien Strömungsquerschnitt und der anliegenden Druckdifferenz besteht, welcher nicht in allen Anwendungsfällen erwünscht ist.A disadvantage of this known differential pressure valve is that there is a nearly linear relationship between the free flow cross-section and the applied pressure difference, which is not desirable in all applications.

Ferner sind eine Vielzahl von Rückschlagventilen bekannt bei denen eine Ventilkugel durch eine Feder vorgespannt im geschlossenen Zustand an einem Ventilsitz anliegt, der durch eine konische oder zylindrisch ausgebildete Drosselöffnung gebildet ist, und im geöffneten Zustand unter Kompression der Feder eine Durchflussöffnung freigibt. Derartige Rückschlagventile zeigen jedoch in aller Regel ein stark von den Erfordernissen bei Kältemittelkreisen abweichendes Öffnungsverhalten.Further, a plurality of check valves are known in which a valve ball biased by a spring in the closed state abuts a valve seat which is formed by a conical or cylindrical throttle opening, and in the open state under compression of the spring releases a flow opening. However, such check valves usually show a very different from the requirements for refrigerant circuits opening behavior.

Derartige Ventile lassen noch Wünsche offen.Such valves still leave something to be desired.

Es ist Aufgabe der Erfindung, ein verbessertes Differenzdruckventil zur Verfügung zu stellen.It is an object of the invention to provide an improved differential pressure valve.

Diese Aufgabe wird gelöst durch ein Differenzdruckventil mit den Merkmalen des Anspruchs 1 bzw. des Anspruchs 2. Vorteilhafte Ausgestaltungen sind Gegenstand der Unteransprüche.This object is achieved by a differential pressure valve having the features of claim 1 and claim 2. Advantageous embodiments are the subject of the dependent claims.

Es wird ein Differenzdruckventil, insbesondere für ein Expansionsorgan einer Kraftfahrzeugklimaanlage, zur Regelung eines Durchflusses eines Fluids in Abhängigkeit einer Druckdifferenz, die zwischen der Hochdruckseite und der Saugdruckseite des Differenzdruckventils anliegt, vorgeschlagen, wobei das Differenzdruckventil ein Drosselelement, das den Durchfluss durch eine Drosselstelle regelt, und eine das Drosselelement in Schließrichtung vorspannende Feder aufweist, und bei dem Drosselelement und Feder derart ausgebildet und eingerichtet sind, dass sich eine überproportionale Abhängigkeit des Durchlassquerschnitts von der anliegenden Druckdiffferenz ergibt.It is a differential pressure valve, in particular for an expansion device of an automotive air conditioning system for controlling a flow of a fluid in response to a pressure difference, which is applied between the high pressure side and the suction pressure side of the differential pressure valve, proposed, wherein the differential pressure valve, a throttle element which regulates the flow through a throttle point, and a spring which biases the throttle element in the closing direction, and in which the throttle element and spring are designed and arranged such that a disproportionate dependence of the passage cross section on the applied pressure difference results.

Dieses Differenzdruckventil ermöglicht bei hohen Druckdifferenzen auf Grund des überproportional großen Strömungsquerschnitts auch eine größere Kälteleistung. Dabei ist es relativ kostengünstig herstellbar. Darüber hinaus kann das Ventil selbstregelnd arbeiten. Es kann daher auf elektronische Regelungen, Sensoren, elektrisch verstellbare Ventile usw. verzichtet werden. Als überproportional kommt dabei insbesondere eine Abhängigkeit A Durchlass ∝(Δp)x mit x=1,1, 1,2, 1,3, 1,4, 1,5, 1,6, 1,7, 1,8, 1,9, 2,0, 2,25, 2,5, 2,75 oder 3 in Betracht.This differential pressure valve allows for high pressure differences due to the disproportionately large flow cross section and a larger Cooling capacity. It is relatively inexpensive to produce. In addition, the valve can work self-regulating. It can therefore be dispensed with electronic controls, sensors, electrically adjustable valves, etc. A particular a dependency passage α (Δ p) x here takes a disproportional with x = 1.1, 1.2, 1.3, 1.4, 1.5, 1.6, 1.7, 1.8, 1.9, 2.0, 2.25, 2.5, 2.75 or 3 into consideration.

Weiterhin wird ein Differenzdruckventil, insbesondere für ein Expansionsorgan einer Kraftfahrzeugklimaanlage, zur Regelung eines Durchflusses eines Fluids in Abhängigkeit einer Druckdifferenz, die zwischen der Hochdruckseite und der Saugdruckseite des Differenzdruckventils anliegt, vorgeschlagen wobei das Differenzdruckventil ein Drosselelement, das den Durchfluss durch eine Drosselstelle regelt, und eine das Drosselelement in Schließrichtung vorspannende Feder aufweist, und wobei das Drosselelement einen kugelförmigen Kopf aufweist. Diese Ausbildung kann sowohl in Alleinstellung, als auch in Kombination mit oben erwähnter Abhängigkeit von Durchlassquerschnitt und Druckdifferenz von Vorteil sein.Furthermore, a differential pressure valve, in particular for an expansion element of an automotive air conditioning, for controlling a flow of a fluid in response to a pressure difference, which is applied between the high pressure side and the suction pressure side of the differential pressure valve, proposed wherein the differential pressure valve, a throttle element that regulates the flow through a throttle point, and a biasing the throttle element in the closing direction spring, and wherein the throttle element has a spherical head. This training can be advantageous either alone or in combination with the above-mentioned dependence on the passage cross-section and pressure difference.

Auch dieses Differenzdruckventil ermöglicht bei hohen Druckdifferenzen auf Grund des überproportional großen Strömungsquerschnitts auch eine größere Kälteleistung. Dabei ist es relativ kostengünstig herstellbar. Auch dieses Ventil kann selbstregelnd im obigen Sinne ausgeführt sein.Also, this differential pressure valve allows for high pressure differences due to the disproportionately large flow cross section and a larger cooling capacity. It is relatively inexpensive to produce. This valve can also be self-regulating in the above sense.

Das Drosselelement des Differenzdruckventils kann einen Schaft aufweisen. Der Schaft des Drosselelements ist bevorzugt zylinderförmig ausgebildet.The throttle element of the differential pressure valve may have a shaft. The shaft of the throttle element is preferably cylindrical.

Der Kopf des Drosselelements ist bevorzugt mittels einer Klebeverbindung zentriert am Schaft angebracht. Es kann sich aber auch als vorteilhaft erweisen, Kopf und Schaft des Drosselelements einstückig auszubilden. Der Schaft hat bevorzugt einen Durchmesser von weniger als 2 mm.The head of the throttle element is preferably mounted centered on the shaft by means of an adhesive connection. However, it may also prove advantageous to design the head and shaft of the throttle element in one piece. The shaft preferably has a diameter of less than 2 mm.

Die Kugeldurchmesser der Drosselelemente betragen bevorzugt zwischen 1,5 und 2,0 mm, der Schaft ist entsprechend kleiner dimensioniert. Da eine hohe Fertigungsgenauigkeit für den Kopf erforderlich ist, sind insbesondere Kugeln aus der Kugellagerfertigung, die relativ kostengünstig bei hohen Genauigkeiten erhältlich sind, geeignet. Die Durchmesserdifferenz des kugelförmigen Kopfes und der durch diesen zu verschließenden Drosselöffnung beträgt - insbesondere bei den genannten Kugeldurchmessern - vorzugsweise maximal 0,01 mm. Auch 0,005 mm, 0,0075 mm, 0,015 mm oder 0,02 mm sind denkbar.The ball diameter of the throttle elements are preferably between 1.5 and 2.0 mm, the shaft is dimensioned correspondingly smaller. Since a high manufacturing accuracy for the head is required in particular balls from the ball bearing manufacturing, which are relatively inexpensive to obtain at high accuracies, suitable. The difference in diameter of the spherical head and the throttle opening to be closed by the latter is preferably not more than 0.01 mm, in particular in the case of the aforementioned ball diameters. Also 0.005 mm, 0.0075 mm, 0.015 mm or 0.02 mm are conceivable.

Bevorzugt ist das Verhältnis von Kugeldurchmesser zu Drosselöffnungsdurchmesser kleiner als 1,02. Ist das Verhältnis kleiner 1, so dringt der Kopf des Drosselelements in die Drosselöffnung ein, weshalb ein axialer Anschlag vorzusehen ist, beispielsweise am Schaft. Auf Grund eines möglichen Verklemmens und Festsetzens ist jedoch ein Verhältnis von Kugeldurchmesser zu Drosselöffnungsdurchmesser von 1,0 ohne andere Maßnahmen eher ungeeignet. Im Übrigens sind auch Verhältnisse von 1,01, 1,03, 1,04, 1,05 oder 1,1 denkbar.Preferably, the ratio of ball diameter to throttle opening diameter is less than 1.02. If the ratio is less than 1, then the head of the throttle element penetrates into the throttle opening, which is why an axial stop is provided, for example on the shaft. However, due to possible jamming and jamming, a ratio of ball diameter to throttle opening diameter of 1.0 is unlikely without other measures. Incidentally, ratios of 1.01, 1.03, 1.04, 1.05 or 1.1 are also conceivable.

Der Kopf des Drosselelements ist bevorzugt saugdruckseitig angeordnet, wobei sich der Schaft des Drosselelements von der Drosselöffnung weg erstreckt, so dass der Schaft nicht durch die Drosselöffnung ragt. Dies hat des weiteren den Vorteil, dass bei einer angeklebten Kugel als Kopf die Klebeverbindung nicht auf Zug, sondern nur auf Druck belastet wird, so dass die Verbindung auch bei langem Betrieb betriebssicher ist. Die schaftseitig angeordnete Feder ist entsprechend ebenfalls saugdruckseitig angeordnet. Hierbei wird auch die Feder bevorzugt auf Druck belastet. Die Anbringung der Feder erfolgt bevorzugt am Schaft und nicht an der Kugel.The head of the throttle element is preferably arranged on the suction pressure side, wherein the shaft of the throttle element extends away from the throttle opening, so that the shaft does not protrude through the throttle opening. This has the further advantage that in a glued ball as a head, the adhesive bond is not loaded on train, but only on pressure, so that the connection is reliable even after long periods of operation. The shaft side arranged spring is also arranged according to suction pressure side. Here, the spring is preferably loaded on pressure. The attachment of the spring is preferably carried out on the shaft and not on the ball.

Der Drosselquerschnitt ist bevorzugt bei großen Druckdifferenzen überproportional größer als bei kleinen Druckdifferenzen, so dass bei maximalem Leistungsbedarf auch ausreichend viel Fluid das Differenzdruckventil durchströmen kann.The throttle cross-section is preferably disproportionately greater for large pressure differences than for small pressure differences, so that at maximum power requirement and sufficient fluid can flow through the differential pressure valve.

Im Folgenden wird die Erfindung anhand eines Ausführungsbeispiels unter Bezugnahme auf die Zeichnung im Einzelnen erläutert. In der Zeichnung zeigen:

Fig. 1
eine Prinzipskizze eines erfindungsgemäßen Differenzdruckventils,
Fig. 2
ein Diagramm des Drosselquerschnitts über dem Differenzdruck, und
Fig. 3
eine Prinzipskizze eines herkömmlichen Differenzdruckventils.
In the following the invention with reference to an embodiment with reference to the drawings will be explained in detail. In the drawing show:
Fig. 1
a schematic diagram of a differential pressure valve according to the invention,
Fig. 2
a diagram of the throttle cross-section over the differential pressure, and
Fig. 3
a schematic diagram of a conventional differential pressure valve.

Ein als Expansionsorgan in einer Kraftfahrzeug-Klimaanlage dienendes Differenzdruckventil 1 weist zur Regelung des Kältemitteldurchflusses (Kältemittel vorliegend R744) eine Drosselstelle 2 auf, wobei die Drosselstelle 2 durch ein kugelförmig ausgebildetes Ende eines Ventilstifts 3, das an der vorliegend zylindrischen Drosselöffnung im geschlossenen Zustand dicht anliegt, gebildet ist. Hierbei beträgt die Durchmesserdifferenz von Drosselöffnung und Kugel 0,005 mm bei einem Kugeldurchmesser von 2 mm.A serving as an expansion element in a motor vehicle air conditioning differential pressure valve 1 has to control the refrigerant flow (refrigerant present R744) a throttle point 2, the throttle point 2 by a spherical shaped end of a valve pin 3, which rests tightly against the presently cylindrical throttle opening in the closed state , is formed. In this case, the diameter difference between the throttle opening and the ball is 0.005 mm with a ball diameter of 2 mm.

Der Ventilstift 3 weist besagtes kugelförmiges Ende, im Folgenden als Kopf 4 bezeichnet, im Bereich der Drasselstelle 2 und einen hiermit mittels Kleben verbundenen zylinderförmigen Schaft auf, der sich von der Drosselstelle 2 weg erstreckt, also nicht in die Drosselöffnung hinein ragt. Der Schaft hat vorliegend einen Durchmesser von 1,5 mm. Am Schaft des Ventilstifts 3 ist eine Feder 5 mit ihrem einen Ende angebracht, welche eine Schließkraft auf den Ventilstift 3 ausübt, so dass bei fehlender oder geringer Druckdifferenz die Drosselöffnung durch der Kopf 4 des Ventilstifts 3 in Folge einer zumindest im Wesentlichen fluiddichten Anlage des entsprechenden konischen Bereiches des Ventilstifts 3 an den Ventilsitze geschlossen ist (vgl. stark schematisierte Darstellung von Fig. 1). Dabei wird die Feder 5 auf Druck belastet.The valve pin 3 has said spherical end, hereinafter referred to as head 4, in the area of the dripping point 2 and a cylindrical shaft connected therewith by adhesive, which extends away from the throttle point 2, ie does not protrude into the throttle opening. The shaft has in this case a diameter of 1.5 mm. On the shaft of the valve pin 3, a spring 5 is attached with its one end, which has a closing force the valve pin 3 exerts, so that in the absence or low pressure difference, the throttle opening is closed by the head 4 of the valve pin 3 as a result of an at least substantially fluid-tight contact of the corresponding conical portion of the valve pin 3 on the valve seats (see highly schematic representation of FIG. 1). In this case, the spring 5 is loaded on pressure.

In Fig. 2 sind die optimalen Betriebspunkte (COP = Coefficient of performance) durch den Bereich zwischen den beiden durchgezogenen Linien dargestellt. Wie aus dem Diagramm ersichtlich, verläuft die Kennlinie eines erfindungsgemäßen Differenzdruckventils 1 mit kugelförmigem Ende in Verbindung mit einer Feder mit der Federkonstante von 23 N/mm im Bereich geringer Differenzdrücke nahe der oberen Bereichsgrenze, imd im weiteren Verlauf verläuft die Kennlinie annähernd mittig. Dahingegen verlaufen die Kennlinien herkömmlicher Differenzdruckventile 101 mit konischem Kopf 104 in Form einer Geraden, so dass je nach Federkonstante stets ein Bereich außerhalb des optimalen Bereichs verläuft. Diese Charakteristik ermöglicht nicht nur bei geringem Bedarf sondern insbesondere auch bei hohem Bedarf an Kältemitteldurchsatz, also im Hochiastbetrieb, eine deutlich verbesserte Kälteleistung.In Fig. 2, the optimum operating points (COP = coefficient of performance) are represented by the region between the two solid lines. As can be seen from the diagram, the characteristic curve of a differential pressure valve 1 according to the invention with spherical end in conjunction with a spring with the spring constant of 23 N / mm in the range of low differential pressures near the upper range limit, imd in the course of the curve is approximately centered. On the other hand, the characteristics of conventional differential pressure valves 101 with a conical head 104 run in the form of a straight line, so that, depending on the spring constant, a region always runs outside the optimum range. This characteristic not only makes it possible to achieve a significantly improved cooling capacity, but also in the case of a high demand for refrigerant throughput, ie in high-load operation.

Steigt bei Betrieb die Druckdifferenz zwischen Saugdruckseite SD und Hochdruckseite HD, so verschiebt sich der Ventilstift 3 entgegen der Federkraft in Richtung Saugdruckseite SD und die Drosselstelle 2 öffnet sich allmählich. Mit weiter steigender Druckdifferenz wird die Drosselöffnung auf Grund der Geometrie des Kopfes 4 deutlich schneller freigegeben, so dass sich ein nicht linearer Zusammenhang zwischen der Druckdifferenz und dem freigegebenen Strömungsquerschnitt, welcher in Zusammenhang mit der Durchflussmenge steht, ergibt (vgl. Fig. 2).If the pressure difference between the suction pressure side SD and the high pressure side HD rises during operation, the valve pin 3 shifts against the spring force in the direction of the suction pressure side SD and the throttle point 2 opens gradually. With a further increasing pressure difference, the throttle opening is released much faster due to the geometry of the head 4, so that a non-linear relationship between the pressure difference and the released flow cross-section, which is related to the flow rate results (see Fig. 2).

Gemäß einer nicht in der Zeichnung dargestellten Variante ist der Durchmesser des Kopfes kleiner als der Durchmesser der Drosselöffnung, so dass der Kopf vollständig in die Drosselöffnung eindringen kann. Am Schaft ist jedoch ein flanschartiger Anschlag vorgesehen, der die Bewegung begrenzt und die Drosselöffnung in der Endstellung verschließt. Hier kann insbesondere eine immer vorhandene Restöffnung realisiert werden, beispielsweise um bei einem Abstellen der Klimaanlage eine übermäßige lokale Druckerhöhung zu vermeiden, wie sie insbesondere bei CO2-Kältemittelkreisläufen ein Problem darstellen kann.According to a variant not shown in the drawing, the diameter of the head is smaller than the diameter of the throttle opening, so that the head can completely penetrate into the throttle opening. On the shaft, however, a flange-like stop is provided, which limits the movement and closes the throttle opening in the end position. Here, in particular an always existing residual opening can be realized, for example, to avoid an excessive local pressure increase when switching off the air conditioning, as they can be a problem especially in CO 2 refrigerant circuits.

Claims (14)

Differenzdruckventil, insbesondere für ein Expansionsorgan einer Kraftfahrzeugklimaanlage, zur Regelung eines Durchflusses eines Fluids in Abhängigkeit einer Druckdifferenz, die zwischen der Hochdruckseite (HD) und der Saugdruckseite (SD) des Differenzdruckventils (1) anliegt, wobei das Differenzdruckventil ein Drosselelement, das den Durchfluss durch eine Drosselstelle (2) regelt, und eine das Drosselelement (3) in Schließrichtung vorspannende Feder (5) aufweist, dadurch gekennzeichnet, dass Drosselelement (3) und Feder (5) derart ausgebildet und eingerichtet sind, dass sich eine überproportionale Abhängigkeit des Durchlassquerschnitts von der anliegenden Druckdiffferenz ergibt.Differential pressure valve, in particular for an expansion element of an automotive air conditioning system, for controlling a flow of a fluid in response to a pressure difference between the high pressure side (HD) and the suction pressure side (SD) of the differential pressure valve (1) is applied, wherein the differential pressure valve is a throttle element, the flow through a throttle point (2) controls, and a throttle element (3) in the closing direction biasing spring (5), characterized in that the throttle element (3) and spring (5) are designed and arranged such that there is a disproportionate dependence of the passage cross section of the applied pressure difference results. Differenzdruckventil, insbesondere Differenzdruckventil nach Anspruch 1, insbesondere für ein Expansionsorgan einer Kraftfahrzeugklimaanlage, zur Regelung eines Durchflusses eines Fluids in Abhängigkeit einer Druckdifferenz, die zwischen der Hochdruckseite (HD) und der Saugdruckseite (SD) des Differenzdruckventils (1) anliegt, wobei das Differenzdruckventil ein Drosselelement, das den Durchfluss durch eine Drosselstelle (2) regelt, und eine das Drosselelement (3) in Schließrichtung vorspannende Feder (5) aufweist, dadurch gekennzeichnet, dass das Drosselelement (3) einen kugelförmigen Kopf (4) aufweist.Differential pressure valve, in particular differential pressure valve according to claim 1, in particular for an expansion element of an automotive air conditioning system for controlling a flow of a fluid in response to a pressure difference between the high pressure side (HD) and the suction pressure side (SD) of the differential pressure valve (1) is applied, wherein the differential pressure valve a Throttling element, which regulates the flow through a throttle point (2), and a spring (5) biasing the throttle element (3) in the closing direction, characterized in that the throttle element (3) has a spherical head (4). Differenzdruckventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das Drosselelement (3) einen Schaft aufweist.Differential pressure valve according to claim 1 or 2, characterized in that the throttle element (3) has a shank. Differenzdruckventil nach Anspruch 3, dadurch gekennzeichnet, dass der Schaft des Drosselelements (3) zylinderförmig ausgebildet ist.Differential pressure valve according to claim 3, characterized in that the shank of the throttle element (3) is cylindrical. Differenzdruckventil nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass der Kopf (4) mittels einer Klebeverbindung am Schaft des Drosselelements (3) angebracht ist.Differential pressure valve according to claim 3 or 4, characterized in that the head (4) by means of an adhesive connection to the shaft of the throttle element (3) is mounted. Differenzdruckventil nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass der Kopf (4) und der Schaft des Drosselelements einstückig ausgebildet sind.Differential pressure valve according to claim 3 or 4, characterized in that the head (4) and the shank of the throttle element are integrally formed. Differenzdruckventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Durchmesserdifferenz des kugelförmigen Kopfes (4) und der durch diesen zu verschließenden Drosselöffnung maximal 0,01 mm beträgt.Differential pressure valve according to one of the preceding claims, characterized in that the diameter difference of the spherical head (4) and the throttle opening to be closed by this is a maximum of 0.01 mm. Differenzdruckventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Verhältnis des Durchmessers des kugelförmigen Kopfes (4) und des Durchmessers der durch diesen zu verschließenden Drosselöffnung kleiner als 1,02 ist.Differential pressure valve according to one of the preceding claims, characterized in that the ratio of the diameter of the spherical head (4) and the diameter of the throttle opening to be closed by this throttle opening is less than 1.02. Differenzdruckventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Kopf (4) des Drosselelements (3) saugdruckseitig angeordnet ist, wobei sich der Schaft des Drosselelements (3) von der Drosselöffnung weg erstreckt.Differential pressure valve according to one of the preceding claims, characterized in that the head (4) of the throttle element (3) is arranged suction pressure side, wherein the shank of the throttle element (3) extends away from the throttle opening. Differenzdruckventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Feder (5) saugdruckseitig angeordnet ist.Differential pressure valve according to one of the preceding claims, characterized in that the spring (5) is arranged suction pressure side. Differenzdruckventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Feder (5) am Schaft des Drosselelements (3) angebracht ist.Differential pressure valve according to one of the preceding claims, characterized in that the spring (5) on the shaft of the throttle element (3) is mounted. Differenzdruckventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Feder (5) auf Druck belastet ist.Differential pressure valve according to one of the preceding claims, characterized in that the spring (5) is loaded on pressure. Differenzdruckventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der effektive Drosselquerschnitt bei großen Druckdifferenzen überproportional größer als bei kleinen Druckdifferenzen ist.Differential pressure valve according to one of the preceding claims, characterized in that the effective throttle cross-section is disproportionately larger at large pressure differences than at small pressure differences. Verwendung eines Differenzdruckventil nach einem der vorhergehenden Ansprüche als Expansionsorgan einer Kraftfahrzeug-Klimaanlage.Use of a differential pressure valve according to one of the preceding claims as an expansion element of a motor vehicle air conditioning system.
EP06009027A 2005-05-13 2006-05-02 Differential pressure valve Withdrawn EP1722176A3 (en)

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EP1722176A3 EP1722176A3 (en) 2007-09-19

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WO2009060465A3 (en) * 2007-07-18 2009-08-27 Vijay Appa Kasar Energy saving expansion device for refrigeration & other industries

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